US3745723A - Grinding machine with loader and work supporting shoes - Google Patents

Grinding machine with loader and work supporting shoes Download PDF

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Publication number
US3745723A
US3745723A US00147815A US3745723DA US3745723A US 3745723 A US3745723 A US 3745723A US 00147815 A US00147815 A US 00147815A US 3745723D A US3745723D A US 3745723DA US 3745723 A US3745723 A US 3745723A
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Prior art keywords
workpiece
shoes
shaft
grinding machine
machine according
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US00147815A
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English (en)
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M Kikuchi
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Toyoda Koki KK
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Toyoda Koki KK
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/35—Accessories
    • B24B5/355—Feeding means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/06—Work supports, e.g. adjustable steadies

Definitions

  • ABSTRACT In a grinding machine of the type in which a workpiece is rotatably supported on a pair of shoes, one of the shoes is fixedly mounted adjacent a grinding wheel, while the other is movably mounted opposite the grinding wheel and downwardly discharges a completed workpiece from a working station when it is moved away from the grinding wheel.
  • a loading arm transfers a yet unoperated-on workpiece from a ready station to the working station where a diameter of the workpiece is measured by a movable feeler mounted on a sizing device contacting the workpiece at a position thereon opposite the two points of contact of the shoes.
  • the present invention relates generally to machine tools and more particularly pertains to a centerless grinding machine of the type where a workpiece is rotatably supported on a pair of shoes.
  • a work-loading locus of the loading arm intersects with a work-unloading locus of the unloading arm, the two arems are justly provided with a relatively long swinging stroke and a motion associated therebetween so as not to interfere with each other, thereby increasing the period of unproductivity in comparision with the grinding period.
  • a spare stroke of escapement-feed movement is generally rendered to a wheel head for preventing the workpiece from striking on the grinding wheel when the workpiece is transferring into the working station or into the delivery station.
  • a still further object of the present invention is to provide a grinding machine with an improved sizing device suitable for external centerless grinding operations of the type where a workpiece is supported on shoes and in which the workpieces are loaded and unloaded in a shorter locus without striking the shoes owing to the retracting movement of one of the shoes.
  • a grinding machine which comprises a bed, a wheel head slidably mounted on the bed for rotatably supporting a grinding wheel, a feed device for moving the wheel head toward and away from a workpiece, a pair of shoes for rotatably supporting the workpiece at a working station adjacent the grinding wheel, driving means for rotating the workpiece, transfer means mounted on the bed for transferring the workpiece into and out of the working station, and a sizing device for measuring the diameter of the workpiece supported at the working station.
  • the transfer means comprises a loading arm rotatably mounted for transferring a workpiece to be ground from a ready station adjacent a loading chute to the working station in association. with the movement of the rear shoe, and an unloading arm rotatably mounted for facilitating the discharge of a workpiece on which the grinding operation is complete from the working station to a discharge chute.
  • FIG. 1 is a front view showing a grinding machine equipped with a loading apparatus constructed according to the present invention
  • FIG. 2 is an enlarged view showing a loader mechanism positioned adjacent to a working station
  • FIG. 3 is a sectional view taken along the line III-III of FIG. 2;
  • FIG. 4 is a sectional view taken along the line IV-IV of FIG. 3;
  • FIG. 5 is a sectional view taken along the line V-V of FIG. 4;
  • FIG. 6 is a sectional view taken along the line VI-Vl of FIG. 5;
  • FIG. 7 is a partly sectioned rear view of the loading mechanism of the invention.
  • FIG. 8 is a schematic diagram of a hydraulic control circuit for the driving mechanism of this invention.
  • FIG. 9 is a fragmentary schematic view of a cam transmission mechanism for swinging a shoe-rotating arm and an unloading arm;
  • FIG. 10 is a schematic view showing the operational relationship and positions of an unloading arm and a rear shoe
  • FIG. 11 is a schematic view of the cam transmission mechanism for swinging the loading arm
  • FIG. 12 is a schematical view showing the operational relationship and position of the loading arm
  • FIG. 13 is a fragmentary schematic view showing the cylindrical cam transmission mechanism for axially driving the loading and unloading arm-shafts and showing the operational relationship of the arm-shafts;
  • FIG. 14 is a schematic view showing a moment caused by an eccentric location of a workpiece
  • FIG. 15 is an enlarged front view showing a sizing device.
  • FIG. 16 is a fragmentary sectional view showing the left side of the sizing device.
  • the reference numeral 1 designates a bed on which a wheel head 2 is slidably mounted to be moved in a longitudinal direction thereon by a conventional feed device 3 which may comprise a fluid actuator, feed screw driven by the fluid actuator, and the like.
  • a grinding wheel compensating device 4 is mounted on the wheel head 2 to move the wheel head 2 a compensating feed amount in accordance with a decrease in the grinding wheel diameter, which is caused by a grinding wheel truing device 5.
  • the truing device 5 is slidably mounted on a base 5c and is transversely moved relative to the wheel head direction of movement by a fluid actuator, not shown, so that a diamond truing cutter 5a thereof may traverse the surface of a grinding wheel in a direction parallel to the wheel axis to dress the grinding wheel S.
  • the truing cutter 5a is rotatably carried by the grinding wheel truing device 5 and is rotated by a drive motor 5b mounted on the rear of truing device 5.
  • the grinding wheel S is rotated by a grinding wheel drive motor 6, the shaft of which is held in driving connection with a grinding wheel shaft 7 through belts and pulleys in a well-known manner.
  • a base 11 On the left portion of bed 1, as viewed in FIG. 1, a base 11 is mounted to fixedly carry a body 12 of a loading fixture opposite the wheel head 2, a headstock 13, and a work support 14, on which a sizing device 160 is adjustably mounted to measure the diameter of a workpiece.
  • the head stock 13 rotatably supports a spindle 15, FIG. 5, to the end of which a rotatable magnetic driver 16 is fixed.
  • a packing plate 17 is secured to the end of the rotatable magnetic driver 16 in co-axial relation with the spindle 15 to be rotated by an electric motor 18 mounted on the headstock 13.
  • the packing plate 17 serves to fix the workpiece W on its ring-shaped end by magnetic attraction to render rotation to the workpiece W which is rotatably carried by a pair of shoes, for example, a front shoe 40 and a rear shoe 43 as shown in FIG. 2. Therefore, the workpiece W is ground at a working station wherein it is rotatably carried by the front and rear shoes 40 and 43 and is rotated by the electric motor 18.
  • a common plane 20 is vertically mounted on the side of body 12 at a predetermined position relative to the body 12 in the same plane of the ring-shaped end of packing plate 17.
  • a loading chute 21 is inclined downwardly in the direction of the grinding wheel and is fixed on the upper portion of the common plane 20 to guide and store workpieces yet unoperated on being supplied from the left end thereof in association with an angle plate 22 and a vertical plate 23.
  • a stop plate 24 is secured to the lower end of the loading chute 21 in parallel relation with the inclination of the loading chute 21.
  • a roller 25 is carried at the lower end of a rod 27 mounted at its upper end on the vertical plate 23 so as to be rotatable in the clockwise direction until the angular position thereof is parallel to the vertical portion of the loading chute 21.
  • a spring 26 is connected to the lower portion of the loading chute 21 and to the rod 27 for uring the roll 25 toward the vertical portion of the loading chute 21 or the foremost workpiece of the stored unground workpieces being in the loading chute 21.
  • the foremost workpiece is suppored at a ready station from which the workpiece may be taken out to be transferred to a working station by a loading arm 30, on the end of which a plug 31 is formed to engage with the bore of the workpiece.
  • the loading arm 30 is secured to the right end of a loading arm-shaft 32 rotatably and slidably mounted on the body 12 as shown in FIG. 3.
  • the front shoe 40 is mounted on the top of a holder 42 so as to be slightly rotatable thereby to fit the peripheral surface of the workpiece.
  • the holder 42 is adjustably. mounted on an attaching plate 41 which is secured to the upper portion of work support 14 fixedly mounted on the base 11.
  • the front shoe 40 is located to be in supporting engagement with the lower right portion of the workpiece W, as viewed in FIG. 2.
  • the rear shoe 43 is pivotally mounted on the right end ofa holder 46 which is adjustably fixed to an attaching plate 45.
  • the attaching plate 45 is securedly mounted on a swivel base 44 which is secured to a flange of a shaft 47, shown in FIG. 5, rotatably mounted on the body 12 in parallel with the loading arm-shaft 32.
  • a connecting rod 48 is pivotally connected to the swivel base 44 by a pin 49 at one end thereof, and at the other end thereof is pivotally connected to the right end of a rotating plate 51 by a pin 52.
  • the rotating plate 51 is secured to a flange of a shoe-rotating shaft 50 rotatably mounted in the body 12 in parallel with the shaft 47.
  • a connecting piece 53 is pivotally mounted on the pin 52 to be connected to one end of a spring 55.
  • the other end of the spring 55 is connected to the upper end of a bracket 54 mounted on the top of body 12.
  • the spring 55 serves to resiliently draw the connecting piece 53 upwardly so that the swivel base 44 is urged toward its right limit formed by the abutting engagement of a stop 57 fixed thereto with a stop 56 projecting out of the body 12.
  • the rear shoe 43 is forwardly moved in a nearly horizontal direction by the clockwise rotations of swivel base 44 owing to the tension of spring 55 and is rearwardly movable upon clockwise rotation of the shoe-rotating shaft 50 in opposition to this tension.
  • the clockwise moment of rear shoe 43 is increased by the link mechanism comprising the aforementioned rotating plate 51, pins 49 and 52, connecting rod 48, and swivel base 44.
  • the tension of spring 55 is not very great, the spring 55 can provide the rear shoe with such rigidity to sufficiently oppose a grinding resistance.
  • the retracting movement of rear shoe 43 is accomplished by a relatively small moment rendered to the shoe-rotating shaft 50, being just enough to oppose the force of spring 55.
  • the front and rear shoes 40 and 43 are adjusted to be positioned so that the rotation center P1 of workpiece W supported at the working station is eccentric by A1 relative to the center P2 of spindle 15, whereby the eccentric moment FAl is rendered to the rotating workpiece between the front and rear shoes 40 and 43.
  • a discharge chute 60 is fixed on the common plate 20, with an inclination to the workingstation.
  • the right end portion of the discharge chute 60 extends into the space between the front and rear shoes 40 and 43 and is adjacent to the workpiece in the working station. Accordingly, a completed workpiece is removed from the working position into the discharge chute 60 because of the eccentric moment FAl rendered thereto when the rear shoe 43 is laterally retracted.
  • An unloading arm 61 is fixed to the right end of an unloading arm-shaft 62 which is rotatably and slidably mounted on the body 12 as is the loading arm-shaft 32.
  • the unloading arm 61 serves to downwardly carry out the completed workpiece from the working station through an abutting engagement with the upper periphery of the ground workpiece and also performs a miscellaneous function in the unloading operation by preventing the ground, or completed,workpiece from flying out of the discharge chute 60, upon being dropped therein.
  • the right end portion of the unloading arm 61 is normally located slightly apart from the upper periphery of the workpiece.
  • the loading arm-shaft 32 is rotatably and axially slidably mounted on the body 12 through bearings 70 and '71 below the working station, while the unloading armshaft 62 is rotatably and axially slidably mounted on the body 12 through bearings 72 and 73 above the working station in parallel with the loading arm-shaft 32, as shown in FIG. 3.
  • a driving shaft 74 is rotatably mounted on the body 12 through bearings 75 and 76 at a position being substantially equidistant from the loading and unloading arm shafts 32 and 62 and the shoerotating shaft 50,FIG.
  • a peripheral cam 77 serving to rotate the to rotate the shoe-rotating shaft 50 and the unloading arm-shaft 62, as best shown in FIG. 6.
  • a peripheral cam 77 Concentrically secured the left portion of driving shaft 74 are cylindrical cams 79 and 80 for causing arm-shafts 62 and 32, respectively, to be axially displaced, as shown in FIG. 3.
  • a swing follower 82 is mounted on a serrated portion of the loading arm-shaft 32 and is restrained against axial movement by sleeves 35 and 36 which are fixed to the body 12. The loading arm-shaft 32 thus is slidably engaged within the swinging follower 82 and is drivingly engaged rotationally with the swinging follower 82.
  • the swinging follower 82 rotatably supports a follower roller 81 in abutting engagement with the peripheral cam 77, as shown in FIGS. 3 and 6.
  • the swinging follower 82 is normally urged toward the peripheral cam 77 by a spring 83, as shown in FIG. 6, so that the follower roller 81 may be held in an abutting engagement with the peripheral cam 77. Therefore, the rotation of driving shaft 74 provides the follower 82 with its swinging movement thereby to rotate the loading armshaft 32.
  • a connecting pin 86 is secured to and projects beyond the swinging follower 85 to engage an elongated slot 89 formed on the lower portion of a connecting rod 88 which is pivotally mounted on a connecting member 87 at the upper end thereof.
  • the connecting member 87 is secured to the unloading armshaft 62 having a counterclockwise moment rendered by a spring 90.
  • the unloading arm-shaft 62 is clockwisely rotated by the pushing movement of connecting pin 86 in abutting engagement with the upper end of the elongated slot 89 when the shoe-rotating shaft 50 is clockwisely rotated in accordance with the profile of peripheral cam 78.
  • a stop member 91 On the right end of unloading arm shaft 62 is fixedly mounted a stop member 91 having an arm 92 thereon, the left side surface 93 of which is adapted to be held in abutting engagement with the rightside surface 96 of the projection of a stop rod which is pivotally mounted on a bracket 94 fixed to the body 12.
  • the stop rod 95 is outwardly urged by a spring 97, FIG.
  • numeral 99 designates an adjusting plate which serves to adequately adjust the backlash in the spline engagement between the swinging follower 82 and the loading arm-shaft 32.
  • an adjusting plate 100 serves to adjust the backlash in the spline engagement between the connecting member 87 and the unloading arm-shaft 62 through a relative rotating torque rendered therebetween.
  • Follower rollers 111 and 112 are rotatably mounted on opposite ends of a supporting rod 110 in abutting engagement with the projecting ends of cylindrical earns 79 and 80, respectively, as shown in FIGS. 3 and 13.
  • the supporting rod 110 is mounted on the loading and unloading arms 32 and 62 through anti-friction thrust bearings 115 and 116 in abutting engagement with the cylindrical earns 79 and 80.
  • the opposite ends of supporting rod 110 are engaged with the left ends of arm-shaft 62 and 32, which are leftwardly urged by compressive springs 113 and 114 disposed respectively between flange portions on arm-shafts 62 and 32 and the body 12, through the anti-friction thrust bearings 115 and 116, respectively.
  • the cylindrical cams 79 and 80 each have the same cam profile and are secured to the driving shaft 74 in a phase difference according to the angular positions of follower rollers 111 and 112 so that the arm-shafts 62 and 32 may be periodically axially moved at the same velocity. Since the aforementioned retaining engagement between the arm 92 and the stop rod 95 is released when the unloading armshaft 62 is rightwardly moved, the arm-shaft 62 is then counterclockwisely rotated by the force of spring 90.
  • the driving mechanism for driving shaft 74 is described herebelow with reference especially to FIGS. 3 and 7.
  • a driven gear 120 is rotatably mounted on the left end of driving shaft 74 and is connected with a clutch member 121 keyed to a tapered portion of driving shaft 74 through a one-way clutch 122.
  • a wedge-shaped notch 123 is formed on the periphery of clutch member 121.
  • a cylinder 126 serving to position the initial angular position of the driving shaft 74 is securely mounted on the rear of body 12 so that an engaging portion 125 formed on the end ofa piston rod 124 may engage with the wedge-shaped notch 123 formed on the periphery of clutch member 121.
  • a piston 103 is slidably received in the cylinder 126 and is urged toward the clutch member 121 by a spring 102 received in a right chamber 128, as viewed in FIG. 7.
  • the driven gear 120 is meshed with a large gear 131 of driving gears 130 to be rotated thereby.
  • the driving gears 130 are rotatably mounted on a bracket 132 secured to the rear of body 12, as shown in FIG. 3.
  • a fluid cylinder 133 which slidably receives a piston 101 and a piston rod 134, on which rack teeth 104 are formed to meshingly engage with a small gear 138 of driving gears 130.
  • the stroke of piston 101 is designed so as to rotate the driving shaft 74 a little more than 360.
  • the CYCLE DIAGRAM shows the retraction and advancement of rear shoe 43, the swinging rise and fall of loading and unloading arms 30 and 61, and the left and right movement of arms 30 and 61 in accordance with the rotation angle of driving shaft 74.
  • the driving shaft 74 is in the angular position of or in an initial position
  • the rear shoe 43 is in the end of advancement, the unloading arm 61 in the end of swing rise, and the loading arm 30 in the end of swing rise.
  • the piston 101 is in the retracted position wherein a limit switch 151 is operated, while the piston 103 of cylinder 126 is in the advanced end wherein a limit switch 153 is operated.
  • the fluid under pressure is applied to a pilot chamber 148 to change a hydraulic change-over valve 143 to its position II, whereby the fluid under pressure from the port B1 is supplied to the right or rear chamber 136 of cylinder 133 through ports P2 and A2 of the hydraulic change-over valve 143. Since the fluid under pressure in the left or front chamber is returned to a reservoir R through a variable throttle 141 and ports A1 and T1, the piston rod 134 is leftwardly advanced at the feed rate defined by the variable throttle 141.
  • the driving shaft 74 is counterclockwisely rotated by the advancement of piston rod 134, whereupon the follower roller 84 follows the rising or working profile portion of the peripheral cam 78 to thereby be clockwisely rotated about the axis of shoe-rotating shaft 50, as best shown in FIG. 9, which is clockwisely rotated against the tension of springs 55,FIG.4, and 90,as best shown in FIG. 9.
  • the swivel base 44 is counterclockwisely rotated about the axis of shaft 47, so that the rear shoe 43 is laterally retracted away from the working station, as shown by the phantom line in FIG. 10.
  • the unloading arm shaft 62 is clockwisely rotated by the clockwise rotation of connecting pin 86 against the tension of spring 90, so that the unloading arm 61 is downwardly swung from the position shown by real line to that shown by phantom line in FIG. 10, thus surely or positively unloading the operated workpiece into the discharge chute 60.
  • the right chamber 128 of cylinder 126 is connected with a port 137 formed on the cylinder 137 to provide a part of fluid under pressure supplied via the port A2 with the right chamber 128 through the port [37, whereby the piston 103 of cylinder 126 is leftwardly moved by the force of spring 102 and the pressure of fluid until the abutting portion 125 is brought into an abutting engagement with the periphery of clutch member 121.
  • the follower roller 81 follows the rising or working profile portion of peripheral cam 77 thereby to be clockwisely rotated about the axis of loading arm-shaft 32 against the force of spring 83, as shown in FIG. 11, so that the loading arm 30 is clockwisely or downwardly swung to transfer the unoperated workpiece W1 held by the plug 31 thereof from the loading to the working station, as shown in FIG. 12.
  • the follower roller 84 At the a2 angular position of rotation of shaft 74, the follower roller 84, FIG.
  • the follower roller 84 follows and is urged toward the falling profile portion continuing from the rising profile portion of peripheral cam 78 by means of spring 55 to be counterclockwisely rotated about the axis of shaft 50, so that the swivel base 44 is clockwisely or forwardly rotated about the axis of shaft 47, FIG. 4, to move the rear shoe 43 toward the grinding wheel S.
  • the unloading arm 61 is retained at its lower limit by the retaining engagement provided between the arm 92 and the stop rod 95.
  • the loading arm which is loading the unground workpiece, reaches the lower limit of its swing motion, or the working station, wherein it holds the workpiece, since the follower roller 81 follows the base profile portion of peripheral cam 77, when the driving shaft 74 is rotated to the a6 angular position. Thereafter, the follower roller 84 follows the moderately falling profile portion to counterclockwisely rotate the swinging follower and thereby feed the rear shoe 43 forward.
  • the rear shoe 43 Since the feed rate of the rear shoe 43 is gradually decreased by the operation of the link means as the rear shoe 43 approaches the workpiece, the rear shoe 43 is moderately brought into engagement with the workpiece so as not to push the workpiece toward the grinding wheel.
  • the driving shaft 74 continues to rotate, the counterclockwise rotation of follower roller 84 is stopped by the stop 56 to thereby maintain a constant predetermined space between the base portion of the peripheral cam 78 and the follower roller 84 till the roller 84 engages with the working profile portion of the cam 78 corresponding to the retraction step of the rear shoe 43.
  • follower rollers 111 and 112 follow the rising terminal profile portions of cylindrical earns 79 and 80, respectively, to rightwardly move arm-shafts 32 and 62 at the same time from the position shown by the real line in FIG. 13.
  • the arm-shafts 32 and 62 reach the position spaced from the left limit thereof by a distance 1, as shown by phantom line, whereby the engagement of plug 31 with the unground workpiece is released, and also the unloading arm 61 is axially displaced to a position to prevent striking of the shoes 40 and 43 in its upward movement.
  • the loading arm 30 is maintained at the loading station, since the follower roller 81 is kept by the force of spring 83 in contact with the inner terminal surface of peripheral cam 77 corresponding to the upper limit of loading arm motion when the driving shaft 74 is further rotated to the a8 angular position.
  • the hydraulic change-over valve 143 is changed to its position I, so that the fluid discharged from the right chamber 136 of fluid cylinder 133 is returned to the reservoir R through check valves 150 and 149, a variable throttle valve 147, and the ports B1 and T1 of magnetic change-over valve 140.
  • the piston rod 134 is moved to the right or rear end at a rapid feed rate set by the variable throttle valve 147 without rotating the driving shaft 74 positioned at its initial position, since the one way clutch 122 is posed between the clutch member 121 keyed to the driving shaft 74 and the driven gear 120 rotatably mounted on the driving shaft 74 in meshing engagement with the driving gear 130.
  • the grinding wheel S is moved by the feed device 3 toward the workpiece to grind it. After the grinding operation is accomplished and the grinding wheel is again retracted, the loading and unloading operations as mentioned above are repeated.
  • the accomplishment of the grinding operation is controlled by a sizing device 160 mounted on the work support 14, as shown in FIGS. 15 and 16.
  • the sizing device 160 comprises a sizing head 162 which pivotally supports a measuring feeler 161 in contacting relation with the peripheral surface of the workpiece W.
  • a displacement detector 163 is mounted in the sizing head 162 in operative engagement with the end of measuring feeler 161 to detect displacement of measuring feeler 161.
  • the sizing head 162 is adjustably mounted on an inclined guideway 165a formed on the top ofa pedestal 165 which is mounted on the base 11.
  • the inclined angle of the guideway 165a is equal to the angle of the line connecting the center of the workpiece supported by the pair of shoes 40 and 43 and the center axis of loading arm-shaft 32, as shown in FIG. 15.
  • a contacting anvil 161a fixed to the end of measuring feeler 161 lies in a plane passing through the rotation axes of the workpiece and the loading arm 30, and the measuring feeler 161 is rotatably supported by a cross spring 166 so as to be displaced along the plane. Accordingly, the working diameter of the workpiece W is measured by the displacement of the measuring feeler 161 which is in contact with a point which is at a position on the peripheral surface of the workpiece opposite to the two points of contact of shoes 40 and 43.
  • the displacement amount of measuring feeler 161 in the measurement by three points of contact is larger than that in the measurement by two points of contact, that is, the displacement of measuring feeler 161 is generally enlarged and is larger than the change of the working diameter to thereby increase the measuring sensitivity of sizing device 160 and to enable the sizing device 160 to perform a highly accurate measurement.
  • the measuring feeler 161 is extended toward the workpiece in substantially parallel relation with the rotation axis of the workpiece, and the point of contact of measuring feeler 161 with the workpiece is on the loading locus of the workpiece W. Therefore, the sizing device 160 may be fixedly mounted on the pedestal 165, since interference thereof with the workpiece is averted in the loading operation associated with the retracting movement of rear shoe 43.
  • the adjustment or displacement of the sizing head 162 along the inclined guideway 165a is performed when the workpiece being loaded is one having a different diameter.
  • the sizing head 162 is moved by a piniondriving shaft which is meshingly engaged with a rack 169 formed on the center portion of the inclined guideway 165a after the release of clamping bolts 167 and 168 so that the sizing point of the changed workpiece is masterset as is well known to those skilled in the art.
  • the displacement detector 163 generally is a differential transformer which comprises a core, not shown, movable in response to the displacement of measureing feeler 161, and energized windings for generating an output signal corresponding to the displacement of the core therewithin.
  • the output signal may be applied to a conventional schmidt circuit, which provides a sizing signal when the output signal is above a preset voltage level corresponding to a desired diameter of changed workpieces.
  • the wheel head 2 is moved away from the ground workpiece by the cutting head amount when a sizing signal is transmitted from the sizing device 160. Simultaneously, the rear shoe 43 is retracted from the working station, and the magnetic driver 16 is deenergized. Thus, the completed workpiece just operated on is unloaded into the discharge chute 60 in response to the retracting movement of rear shoe 43. A little after this movement, the loading arm 30 starts the loading operation thereof and in turn the rear shoe 43 starts to move back into the working station or toward the front shoe.
  • the rear shoe 43 is disposed and strongly fixed at the forward limit of movement thereof being restrained by the stop 56 through the spring 55 and the link mechanism.
  • the magnetic driver 16 is reenergized to come into driving engagement with the new workpiece mounted on the shoes 40 and 43.
  • the grinding operation is commenced by the cutting feed of the wheel head 2 and the rotation of the magnetic driver 16.
  • the loading and unloading arms 30 and 61 are returned to their upper limits or normal positions.
  • the wheel head 2 is forwardly moved for grinding the workpiece without the conventional rapid feed movement of a spare escapement-stroke.
  • the sizing device 160 transmits a sizing signal to retract the wheel head 2.
  • the magnetic driver 16 is then deenergized, and the rear shoe 43 is moved away from the workpiece just operated on, thus dicharging the workpiece into the discharge chute 60 through the operation of the unloading arm 61.
  • a grinding machine of the type having a bed, a grinding wheel, and a headstock, comprising;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Feeding Of Workpieces (AREA)
US00147815A 1970-05-30 1971-05-28 Grinding machine with loader and work supporting shoes Expired - Lifetime US3745723A (en)

Applications Claiming Priority (1)

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JP45046542A JPS4836397B1 (enrdf_load_stackoverflow) 1970-05-30 1970-05-30

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US3745723A true US3745723A (en) 1973-07-17

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US (1) US3745723A (enrdf_load_stackoverflow)
JP (1) JPS4836397B1 (enrdf_load_stackoverflow)
DE (1) DE2126506A1 (enrdf_load_stackoverflow)
FR (1) FR2093900A5 (enrdf_load_stackoverflow)
GB (1) GB1306041A (enrdf_load_stackoverflow)

Cited By (4)

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US4519166A (en) * 1982-08-18 1985-05-28 Georg Muller Kugellagen Fabrik K.G. Workpiece handling apparatus for grinding machines
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CN116810422A (zh) * 2023-07-21 2023-09-29 江苏洲佳建设工程有限公司 一种建筑模板辅助加工装置
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CN109048559A (zh) * 2018-07-02 2018-12-21 滁州亿扬零部件制造有限公司 一种适用于小型零部件的表皮打磨工装
CN112958808B (zh) * 2021-03-16 2022-05-10 温州神一轴业股份有限公司 一种用于轴料钻中心孔的钻床
CN115816178A (zh) * 2023-02-03 2023-03-21 江苏天叙照明集团有限公司 一种铸造灯杆打磨机
CN119734202A (zh) * 2025-03-06 2025-04-01 凯瑞特阀业集团有限公司 一种多晶硅球形调节阀阀芯精密定位加工工装

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US2635395A (en) * 1951-05-19 1953-04-21 Bryant Grinder Corp Machine for grinding internal surfaces concentric with external surfaces
US2793479A (en) * 1954-12-07 1957-05-28 Bryant Grinder Corp Internal grinding machine
US2912798A (en) * 1958-11-14 1959-11-17 Cincinnati Milling Machine Co Loader for machine tool
US2969623A (en) * 1957-12-30 1961-01-31 Cincinnati Milling Machine Co Size gauging device
US3158965A (en) * 1959-11-25 1964-12-01 Heald Machine Co Apparatus for grinding

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US2635395A (en) * 1951-05-19 1953-04-21 Bryant Grinder Corp Machine for grinding internal surfaces concentric with external surfaces
US2793479A (en) * 1954-12-07 1957-05-28 Bryant Grinder Corp Internal grinding machine
US2969623A (en) * 1957-12-30 1961-01-31 Cincinnati Milling Machine Co Size gauging device
US2912798A (en) * 1958-11-14 1959-11-17 Cincinnati Milling Machine Co Loader for machine tool
US3158965A (en) * 1959-11-25 1964-12-01 Heald Machine Co Apparatus for grinding

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Publication number Priority date Publication date Assignee Title
US4519166A (en) * 1982-08-18 1985-05-28 Georg Muller Kugellagen Fabrik K.G. Workpiece handling apparatus for grinding machines
CN108673341A (zh) * 2018-08-01 2018-10-19 温岭市正大工业机器人有限公司 快速定心夹紧机构
CN108673341B (zh) * 2018-08-01 2024-03-15 台州小助手智能科技有限公司 快速定心夹紧机构
CN116810422A (zh) * 2023-07-21 2023-09-29 江苏洲佳建设工程有限公司 一种建筑模板辅助加工装置
CN117161857A (zh) * 2023-11-03 2023-12-05 南通蓬盛机械有限公司 用于加工瞄准镜物镜筒的打磨机
CN117161857B (zh) * 2023-11-03 2024-03-12 南通蓬盛机械有限公司 用于加工瞄准镜物镜筒的打磨机

Also Published As

Publication number Publication date
GB1306041A (enrdf_load_stackoverflow) 1973-02-07
JPS4836397B1 (enrdf_load_stackoverflow) 1973-11-05
FR2093900A5 (enrdf_load_stackoverflow) 1972-01-28
DE2126506A1 (de) 1971-12-09

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